Controllable deflection roll



1963 Y c. M. WESTBROOK 3,106,153

CONTROLLABLE DEFLECTION ROLL Filed March 9, 1961 2 Sheets-Sheet 1INVENTOR. [krl M 10/95 Lfiraa M f w ATTORNEYS Oct. 8, 1963 c. M.WESTBROOKI CONTROLLABLE DEFLECTION ROLL 2 Sheets- Sheet 2 Filed March 9,1961 IN VEN TOR. (kw! M. We: trawfi,

ORNE YS United States Patent 3,166,153 CQNTRGLLABLE DEFLECTEQN RQLL CarlM. Westbrook, Beloit, Wis, assignor to Beioit Iron Works, Beloit, Wis, acorporation of Wisconsin Filed Mar. 9, H61, Ser. No. 94,576 12 Claims.(Cl. 100-155) v The present invention relates broadly to the papermaking and related arts, and is more particularly concerned with a rollstructure and deflection means for use therewith featuring a thermallyexpansible support member mounting a roll shell and applying forces tothe shell to accurately counteract the forces tending to deflect thesame.

At different stages during the course of paper manufacture it is ofcourse known to employ roll structures of various types for performanceof diverse functions.

Illustrative of such rolls are wire drive rolls, plain press rolls,smoothing press rolls, pressure rolls, breaker stack rolls, size pressrolls, pull rolls, calender rolls and the like. Each of the stated typesof rolls has in common, for the purposes of the instant description, theuse therewith of means normally contacting the roll and tending todeflect the centroidal axis thereof.

To illustrate, drive dr-olls mounted to engage the loop of the formingwire in a Fourdrinier type paper making machine engage the surface ofthe wire, and the weight of the roll coupled with an applied loadarising from the resistance of the wire to being driven produce a forcecomponent which tends to deflect the drive roll in a directiondownwardly and toward the oncoming forming wire. As well, in press rollcouples and in other roll arrangements wherein at least a pair of rollsare in nip-defining relationship, the algebraic summation of the weight,the nip forces, the bending moments produced by the journal loading, andtorque (if any) tends to produce in each of such rolls a curvature ofits centroidal axis, in accordance with well known laws of flexure ofmaterials. It is common to attempt to counter this effect by crowning,i.e., by grinding the roll slightly barrel shape in an amount andcurvature calculated to offset the curvature under operating conditions.

The normal deflection, when concave toward the wire wrap, on a wiredrive roll, if not relieved, tends to cause the off-running portion ofthe forming wire to be compacted or squeezed laterally, which increasessubstantially the wear on the wire. The initial investment in a formingwire is very substantial, but even more important, the production lossduring wire replacement is frequenty enormous.

Specifically as to press rolls, a different problem exists. Productionschedules for many paper machines require relatively frequent changes inthe type and grade of product. Certain grades of paper demand that thepressing and other treatment not reduce significantly the thickness orcaliper of the web, and this in turn requires that the nip loads in apress couple be relatively light. On the other hand, certain other paperproducts required from the same paper machine permit or even demand moresevere pressing, and in order to achieve some meas ure of versatilitywith the same paper machine, one practice followed by the art toaccomplish the noted changes is the removal of the press rolls forregrinding to a dilferent amount of crowning. Obviously, this practiceis also both expensive and time consuming. And as will be later noted,crowning of the roll causes differences in the surface speed of the rollbetween the central and end portions of the roll, which is often harmfulto the function of the press.

It is accordingly an important aim of the instant invention to provide aroll assembly embodying therein 3,l%,l53 Patented Got. 8, 163

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novel means to counteract the forces tending to deflect the roll.

Another object of this invention lies in the provision of an improvedpaper machine arrangement comprising a roll, means normally contactingthe roll and tending to deflect the centroidal axis thereof, and supportmeans in bearing relation with the roll generally centrally of theinterior thereof and extending outwardly from its opposite ends andsusceptible of deflection upon the application of a controlled heatthereto for applying forces to the roll to counteract the forces tendingto deflect the same.

Still another object of this invention is to provide apparatus forcontrolling deflection in a roll member and which comprises a thermallyexpansible support member coextensive with and mounting the roll member,and means for applying heat to a portion of the support member todeflect the same and impart a deflecting force to the roll member.

A further object of the instant invention lies in the provision of aroll assembly, and which includes a shell having normally a centraldeflection, a thermally expansible support member received by andextending outwardly from opposite ends of the shell for mounting saidshell, bearing means between said support member and the shell generallycentrally thereof, and means for applying heat to the support member todeflect the same and impart a deflecting force to the shell generallycentrally thereof in opposition to the normally central deflection.

An even further object of the present invention is to provide apparatusof the foregoing character, and which further features sensing meansresponsive to the thermal expansion of the support member and indicatingthe change in length therein, whereby deflection 0f the shell may bemeasured.

Other objects and advantages of the invention will become more apparentduring the course of the following description, particularly when takenin connection with the accompanying drawings.

In the drawings, wherein like numerals designate like parts throughoutthe same:

FIGURE 1 is a more or less diagrammatic view showing forces applied to adrive roll in a Fourdrinier type paper making machine;

FIGURE 2 is an exaggerated essentially diagrammatic top plan view of adrive roll mounting of the prior art;

FIGURE 3 is an essentially diagrammatic side elevational view of thedevice of FIGURE 2;

FIGURE 4 is a diagrammatic top plan view drawn along the lines of FIGURE2, but showing deflection means constructed in accordance with theprinciples of this invention.

FIGURE 5 is a longitudinal vertical sectional view taken substantiallyalong the line VV of FIGURE 4; and

FIGURE 6 is a transverse vertical sectional view taken substantiallyalong the line VIVI of FIGURE 5.

The controllable deflection roll of this invention will be nowspecifically described in connection with certain problems presented inthe paper making arts, however, it will be immediately apparent that thepresent concepts also produce substantial improvements on rolls used insteel mills and other industries. As well, the invention is of importantapplication in combination with conventional loading applied at thejournal-s of a mating roll and/or with a straight roll or a roll havingconventional crown. By regulating the forces produced by the thermallyexpansible support member of this invention, in cooperation with journalloading, there is thus obtained a novel manner of altering the shape ofthe nip pressure profile.

It has earlier been the accepted practice in a Fourdrinier type papermaking machine to drive the forming wire through the suction couch roll,however, recently it has been found advantageous to use the return rollsas drive rolls and to drive the wire with drive rolls mounted outsidethe loop of the wire and engaging the outer surface of the wire. In thecase of such rolls the wire passes over the top of the drive rolls.

While these changes in the wire drive arrangement have resulted in amuch longer wire life, it is apparent that many further improvements canbe made. Specifically, it is known that the drive roll has a tendency todeflect from its own weight and forces applied thereto, and suchdeflection curvature causes at least a compacting together of the wovenelements of the wire, and in some cases an overlapping or ridging ofsmall portions of the wire. These conditions markedly increase wear onthe wire and may destroy its usefulness.

This may be more fully understood when reference is made to FIGURE 1,which is a diagram showing some of the forces applied to a drive roll20. The wire 12 (traveling in the direction indicated by the arrow)passes over the top of the roll and wraps the roll 20 by a total angleof wrap of 2 alpha. As here shown the oncoming side 12b of the wire 12wraps the roll 20 over the angle alpha and the off-running side 3120 ofthe wire also wraps the roll over the angle alpha with the dividing linev therebetween being a substantially vertical line passing through thecenter of the roll 20. The tension on the wire 12 thus applies a forcein an essentially downward verticfl direction indicated by the arrow A.

The weight of the roll 20 also applies a force in the direction of thearrow A. It will be appreciated that loading forces such as the Weightof the roll and the tension on the wire 12 load the roll 20 as a beam.And the roll 20 has a substantial length compared to its diameter. Forexample, in a typical paper machine the roll 20 Will be approximately 20feet long and approximately 1 /2 feet in diameter.

It will further be appreciated that when the roll 20 is rotated in thedirection indicated by the arrow (on the roll 24)) there is a loadapplied across the top of the roll in a direction generally tangentialto the roll portion wrapped by the wire 12. The wire 12 resists beingdriven to this extent so as to apply this load to the roll 20 and thisload applies generally in the direction of the line of force B. Theresulting sum of all of the loads applied to the roll 2i) may beindicated by the force line C and this generally is the direction inwhich the roll 20 tends to deflect the centroidal axis thereof. It willbe noted that the roll tends to deflect in a direction downwardly andtoward the oncoming wire 12b).

Referring now to FIGURES 2 and 3, it will be seen that the deflection isshown in exaggerated form. In FIG- URE 2 the roll 219 is shown rotatablydriven by drive means 23 (indicated diagrammatically) and both journals23 and 24 rotatably mounted in bearing means 25. The wire 12 passes overthe top of the roll 29; and it will be seen that the roll 2% isdeflected in its central portion 29:: backwardly or in the direction ofthe oncoming side 12b of the wire 12. Gr as may be otherwise stated, theindicated centroidal axis 290 is deflected. As shown in FIG- URE 3, thecentral portion 29a of the roll 20 is deflected off-center from thedrive means 23 and the extreme edge of the roll, which is full linemarked 20. The central portion 20a is deflected toward the oncoming side12b of the wire and also downwardly. The curvature of the roll surface,although not visible, reorients the driving effort forces so that theirlines of action tend to converge, resulting in the application to thewire of transverse forces in the directions indicated by the arrows E ofFIGURE 2. Thus, although the oncoming side 12b of the wire 12 may haveno transverse forces applied thereto and the wire 12 may be traveling insubstantially a straight line in a plane generally tangential to theroll 20 (as indicated by the arrows 12), as the wire 12 passes over thebowed or deflected roll 29, there is a tendency to narrow the wire atthe off-running side 12c (as indicated by the arrows c). This transversecompression of the oil-running wire side 12c tends to ofler anopportunity for the wire to ridge, particularly if any slight forces maybe applied normal to the plane of the wire (for example, by fibers orsome dirt or impurity adhering to the roll 20 and passing between theroll 20 and the wire 12).

In FIGURES 4, 5 and 6, there is shown an exemplary embodiment of theinstant invention for relieving deflection in a roll member. The rollassembly illustrated therein is designated generally by the numeral 30,and comprises a cylindrical shell 31 mounted for rotation by bearingmeans 32a-c upon a stationary thermally expansible support membergenerally identified as 33, which is received by the shell 31 andcentrally positioned within the shell 31. The central bearing element32b may and often preferably is replaced by a pair of centrally disposedalloohiral bearing elements (not shown) which are positioned on bothsides of the 32b position at approximately the /2, or points. The member33 may take various forms, and may be a bi-metallic element or may havethe specific construction of FIGURE 6.

As appears therein, the thermally expansible support member may beformed of a pair of generally flat steel plates 34 and 35 one face ofwhich is milled or otherwise formed with transversely spaced andlongitudinally extending slots or grooves, which form fluid flowpassages 36a-e when the plates 34 and 35 are assembled in face-tofacerelation. Welding techniques may be employed to effect the securementbetween the plate members 34 and 35, and to assure a fluid-tight sealtherebetween gasket means (not shown) may be used. In any event, theplate member 34 and 35, if welded rather than bolted one to the other,are formed into a unitary structure along seam lines 37 and -38 at thetop and bottom thereof. Each plate member has a length greater than theaxial length of the shell member 31, as appears in FIGURES 4 and 5, toprovide end portions 33a and 33b on the thermally expansible supportmember which extend outwardly from opposite ends of the shell 31.

The opposed end portions 330: and 33b of the support member 33 arereceived in self-aligning bearing means 39 and 46, respectively, and itmay be noted from FIGURE 5 that the bearing means 39 is mounted in afixed support 41, while the bearing means 40 at the opposite end thereofis mounted in a movable support 42. The latter support is provided inorder to compensate for thermal expension of the support member 33, andfor this purpose the support 42 rides upon a plurality of rod or ballmembers 43 slidable or movable upon a fixed contoured base plate 44. Ofcourse, in substitution for the elements 43 and 44 shown, there could beutilized a suitable slide arrangement.

As was stated, the cylindrical shell 31 rotates about the stationarynon-rotatable support member 33 upon bearing means 32a-c spaced alongthe axis of the shell 31. Each bearing means may include a pair ofradially spaced annular races 45 and 46 (FIGURE 6) housing therebetweena plurality of rolling elements 47. To preclude the possibility ofcollapse of one or more of the bearing rings 45 and 46 during rotationof the shell 31 about the support member 33, there may be positionedbetween the flat faces of the plate members 34 and 35 and the inner racering 45 a pair of semi cylindrical spacer members 48 and 49.

The end of the cylindrical shell 31 adjacent the movable support 42mounts thereon a plate or cap member 50 receiving therethrough the endportion 33b of the support member 33 with sufiicient spacingtherebetween to avoid any interference during shell rotation. Theopposite end of the shell 31. rigidly mounts a cap or plate member 51shaped to'provide a collar portion 51a having formed thereon sprocketteeth 5115 over which is trained a sprocket 52 which wraps a sprocketwheel 53 mounted upon shaft means 54 driven in rotation by motor means55. While motive means 55 are illustrated to impart rotation to theshell member 31, this may not at all times be required since movement ofthe forming wire 55 (FIGURE 4) may be suflicient to rotatably drive theshell 31.

The support beam 33 is desirably constituted of a steel or any othermetallic bar material having a coeflicient of thermal expansion suchthat when a portion of the metal beam is selectively heated or heatedand cooled, that portion of the beam member deflects an amountsuflicient to exert forces on the shell member 31. of a magnitude tooppose the forces causing the normal central deflection in the shell 31.The normal central deflection in the shell member 31 may be caused bythe Weight of the roll coupled with an applied load arising fromresistance of the forming wire to be driven, as was discussed inconnection with FIGURE 1 to 3, or if the shell 31 forms a part of apress roll couple or other roll arrangements wherein at least a pair ofrolls are in nip-defining relation, the central deflection forces may beconstituted from the algebraic summation of the weight, the nip forces,the bending moment produced by the journal loading and any torque whichmight be present. In any event, selective expansion of the upper portionof the support beam 33, with or without selective contraction of thelower beam portion, causes a bowing of the beam 33 in an upwarddirection, and through the bearing connection at 321;, a deflection orbowing of the shell 31 is effected. The expansion and bowing of thesupport beam 33 are of course almost imperceptible to the human eye, andthe upward forces are generally only of a magnitude sufficient tocounterbalance the forces causing the original central deflection.

It was stated herein above that the thermally expansible support membercould take the form of a bi-metallic element, although conveniently thesupport beam is constituted in the manner specifically described inconnection with FIGURE 6. The milled passages 36tz-e may be five innumber as illustrated, although it is of course appreciated that thisnumber may be varied. In an illustrative arrangement, the upper threepassages 36ac may receive a fluid such as water heated to the desiredtemperature level, while the lower two passages 36d and 36e receive coldwater.

The hot water passages Eda-c have connected thereto conduit means 57ac,while the lower two passages have fluid communicated thereto by conduitmeans 57d and 57:2. All conduits 57 are connected to manifold means 58provided with a separator ordivider member 58a. In this manner theinterior of the manifold 58 is divided into a hot water compartment 59and cold water compartment 60, and connected to the named compartmentsare conduit means 61 and 62, eachhaving therein valve means 63 and 64,which may be thermally responsive and control the admission of fluid tothe compartments 5 9 and 6t) and ultimately to the passages 36a-e in thesupport beam 33.

In order to accurately control the amount of heat applied to the supportbeam 33 and to thereby not only regulate but measure the extent of thebeam distortion, means are herein provided for measuring the changes inupper and lower pontions of the beam length occasioned by either heatapplication or loading by external forces. Such means also may be usedto measure the resultant roll de' ection. Such means, as appears inFXGURE 5, comprises a pair of strain gauges 65 and 66 suitably attachedgenerally centrally of the axial length of the beam 33 and inwardly ofthe marginal side portions thereof in order to sense length changes ofthe beam along the longitudinal portions afiected by the hot or coldfluids. In other words, the strain gauge 65 detects length changes inthe upper portion of the beam 33 by externally applied forces and/or theheated passages 36ac, while the strain gauge 66 senses length changes inthe beam in the lower portion thereof and which arise from externalloading and/or the flow of coolant through the passages 36d and 362.Thus, both strain gauges 65 and 66 under conditions of actual loading byexternal means, as by wire weight and drag plug roll weight, wouldnormally sense approximately equal beam length changes, whereas when hotfluid is flowed into the upper passages 36a-c and cold fluid into thelower passages 35d and 36e, the strain gauge 65 detects the increase inbeam length in the upper portion caused by expansion and the gauge 66the contraction resulting from the input of cold fluid.

The strain gauges 65 and 66 are connected by wires 67 suitably attachedto the support beam 33 and extending outwardlythrough the cap meansStito suitable in dicating means 68 and 69. Such indicating means may begalvanometers, although other instruments may be employed for thispurpose. Advantageously, conventional control means (indicated in dottedlines at 71) responsive to the strain gauge signals means 6h, 69' may beemployed to maintain a predetermined total shell deflection bytemperature control via such valves 63, 64.

As applied to a single roll exemplified by a wire drive roll or felt ina drier section, the deflection sensing means of this invention wouldnormally be utilized by loading the roll shell 31 and support beam 33externally, as by the roll weight coupled with the load arising fromresistance of the wire to be driven. The change in length of therespective portions of the beam by the external loading would then bemeasured by the strain gauge 65 and by the gauge 66. Hot fluid wouldthen be circulated through the passages 3651-0, and coolant caused toflow through the lower passages 36d and 36e. The temperature of the hotfluid and cold fluid would then be controlled to provide a zero straingauge reading. Of course, and as required, the fluids are continuouslycirculated through the passages 36, and for this purpose the passagescommunicate at one end with discharge conduits Thane. Pump means (notshown) would of course be provided to produce the desired continuouscirculation.

The instant inventive concept also is productive of numerous advantagesin roll couples. As applied to a press roll couple, wherein thealgebraic summation of the weight, nip forces, bending moments producedby jourrial loading, and torque (if any) tend to produce a curvaturealong the centroidal axis, the deflection control means herein describedwould be utilized as follows. in such an application, the support beam33 would be distorted or upwardly bowed by the application of heat,coolant also being used in the lower passages 36d and 36a. The lengthchange of the relative portions of the beam resulting from thedistortion would then be measured by the strain gauge es and by thegauge es. The roll shell 31 and support beam 33 would then be loaded toa zero strain gauge galvanometer reading by the application of theforces tending to cause normal central deflection, such as the rollweights and journal loadings. Of course, a similar technique could beutilized in a calender stack, or in any other application wherein atleast a pair of rolls are in nip-defining relationship.

The structural association described could be modified to incorporate apair of strain gauges in a bridge circuit, one of the gauges beingtemperature sensitive and providing a zero reading at maximum heatinput, and the other gauge being load sensitive and providing a zeroreading at no external load. The bridge circuit could embody atemperature compensator, and actual loadings in this environment wouldbe charted on a computer circuit.

t may now be seen that by the support beam and associated structuredescribed forces may be applied which precisely correspond to the weightof the roll body, the wire tension, nip loading, and the like, withoutsignificant force couples which would introduce changes of shape in theflexure curve of the roll. As applied to a wire drive roll, illustratedin FIGURES 4 and 5, there is completely eliminated any tendency of theoff-running portion of the forming wire to be compacted laterally. Thisappears in FIGURE 4, and is shown by the arrows d, clearly indicatingthe wire leaves the roll shell 31 in full width with the driving forcesoriented non-convergently.

In addition to effectively counteracting the normal roll deflection, theroll assembly 30 is characterized by an absence of undesirable bendingmoments and the provision of an essentially true or straight roll.Additionally, there is eliminated the earlier problem of grinding toachieve a particular crown. To illustrate, different grades of paperrequire different nip loads, and it is also necessary that differentgrades of paper be produced on the same paper machine. Furthermore, itis often desirable to alter the nip loading for other reasons. However,to accomplish this it has previously been required to remove the pressrolls for regrinding to a diiierent amount of crowning, crowning ofcourse being practiced in an endeavor to obtain uniform nip loads acrossthe contacting roll faces, or to accept a degree of non-uniformity asthe expedient. To remove the press rolls and effect regrinding isobviously a time-consuming and expensive procedure. However, byutilization of the roll assembly 3% as the lower or even as both the topand bottom rolls in a press couple, deflection is efiectivelycounteracted or relieved to provide uniform nip pressures entirely alongthe roll contact line.

The concept of this invention is productive of highly advantageousresults as applied to either a single roll or to a plurality of rolls innip-defining relationship. It is accordingly believed quite apparentthat this invention is susceptible of numerous modifications withoutdeparting from the novel concepts thereof, as for example, means may beprovided for shifting the support beam to compensate for non-verticalloading.

I claim as my invention:

1. Apparatus for controlling deflection in a roll memer, comprising athermally expansible support member coextensive with and mounting saidroll member, and first conduit means for applying heat to an axiallyextending portion of said support member and second conduit means forwithdrawing heat from another radially spaced axially extending portionof said support member, thereby to deflect the support member and imparta deflecting force to said roll member.

2. A roll assembly, comprising a shell subject to forces tending tocause deflection, a support beam received by and mounting said shell andextending outwardly from the opposite ends thereof for receptionbysupport members for the assembly, means between said beam and saidshell for transmitting forces from the beam to the shell, means forapplying heat to an axially extending portion of said beam to distortthe same and thereby impart to said shell forces in opposition to theforces tending to cause deflection, and control means connected to saidbeam and sensing changes of length therein resulting from heating saidbeam.

3. A roll assembly, comprising a shell subject to forces tending tocause deflection, a support beam received by and mounting said shell andextending outwardly from the opposite ends thereof for reception bysupport members for the assembly, means between said beam and said shellfor transmitting forces from the beam to the shell, means for creating atemperature differential between axially extending portions of the beamfor distorting said beam to impart to said shell forces in opposition tothe forces tending to cause deflection, and means connected to said beamand sensing changes of length therein resulting from said distortion,whereby the deflection of the shell may be controlled.

4. A roll assembly, comprising a shell having normally a centraldeflection, a thermally expansible support rnem- -ber received by andmounting said shell and extending outwardly from the opposite endsthereof to support eleents, bearin means between said support member andsaid shell generally cen rally thereof, and first conduit means forapplying heat to an axially extending portion of said support member andsecond conduit means for withdrawing heat from another radially spacedaxially extending portion of said support member, thereby to distort thesupport member and deflect said shell generally centrally thereof inopposition to the normally central deflection.

5. A roll assembly, comprising a shell having normally a centraldeflection, a thermally expansible support member received by andmounting said shell and extending outwardly from the opposite endsthereof to support elements, bearing means between said support memberand said shell generally centrally thereof, means for applying heat toan mially extending portion of said support memher to distort thesupport member and deflect said shell generally centrally thereof inopposition. to the normally central deflection, and means connected tosaid support member and sensing changes of length therein resulting fromheating said member, whereby deflection of the shell may be measured.

6. A roll assembly, comprising a shell having normally a centraldeflection, a thermally expansible support member received by andmounting said shell, said support member having a plurmity ofsuperimposed spaced axially extending passages formed therethrough,bearing means between said support member and said shell generallycentrally thereof, means for flowing a heated fluid through theuppermost passages in said support member and cooling fluid through thelower passages to distort the support member and deflect said shellgenerally centrally thereof in opposition to the normally centraldeflection, and means connected to said support member and sensingchanges of length therein resulting from heating said member.

7. A roll assembly, comprising a shell having normally a centraldeflection, a thermally expansible support member received by andmounting said shell and extending outwardly from the opposite endsthereof, said support member having a plurality of spaced axiallyextending passages formed therethrough, bearing means between saidsupport member and said shell generally centrally thereof, means forflowing a heated fluid through the passages in one portion of saidsupport member, means for supplying a coolant to the passages in anotherportion of said support member, said heated fluid and said coolant whenflowing in said passages distorting the support member and deflectingsaid shell generally centrally thereof in opposition to the normallycentral deflection, and means connected to said support member andsensing changes of length in said portion resulting from heating andcooling said member.

8. A roll assembly, comprising a shell having normally a centraldeflection, a coaxially extending beam member protruding outwardly fromopposite ends of said shell, said beam member having a bank of axiallyextending fluid flow passages extending completely therethrough, bearingmeans receiving opposite ends of said beam memer, support means for saidbearing means, means between said beam and said shell for transmittingforces from the beam to the shell, conduit means communicating with thepassages in the upper portion of said beam member for supplying heatedfluid thereto for distorting said beam and deflecting said shellgenerally centrally thereof in opposition to the normally centraldeflection, and strain gauge means attached to said beam member fordetecting changes of length in said portion resulting from heating saidmember.

9. A roll assembly, comprising a shell having normally a centraldeflection, a coaxially extending beam member protruding outwardly fromopposite ends of said shell, said beam member having a bank of axiallyextending fluid flow passages extending completely therethrough, bearingmeans receiving opposite ends of said beam member, support means forsaid bearing means, means hetween said beam and said shell fortransmitting forces from the beam to the shell, first conduit meanscornmunica-ting with the passages in the upper portion of said beammember for supplying heated fluid thereto, second conduit meansconnected to the passages in the lower portion of said beam member forflowing coolant therethrough, said heated fluid and said coolant whenflowing in said passages distorting the support member and defleetingsaid shell generally centrally thereof in opposition to the normallycentral deflection, strain gauge means attached to said beam memberalong the upper and lower portions thereof for detecting changes oflength in said portion resulting from heating and cooling said member,and instrument means indicating the length changes detected by saidstrain gauge means.

10. A roll assembly comprising a shell subject to forces tending tocause deflection, a support beam re ceived by and mounting said shelland extending outwardly from the opposite ends thereof for reception bysupport members for the assembly, means between said beam and said shellfor transmitting force from the beam to the shell, first conduit meansfor applying heat to an axially extending portion of said beam, andsecond conduit means radially spaced from said first conduit means forwithdrawing heat from said beam, whereby the first and second conduitmeans may distort the beam and impart to the shell forces in oppositionto forces tending to cause deflection.

11. A roll assembly, comprising a shell that is subject to deflection inresponse vto a load applied thereto, a support member having separateaxial passages therein and received by and mounting said shell, bearingmeans between said support member and said shell generally centrallythereof, and separate and independent conduit means for flowing a heatedfluid through one of such axial passages in the support member and forflowing cooling fluid through another separate and distinct axialpassage in said support member radially spaced from the axial passagereceiving the heated fluid, thereby to distort the support member anddeflect said shell in opposition to said deflection.

12. A roll assembly, comprising a shell tending to deflect in responseto a load applied thereto, a beam member generally aligned with thecentroidal axis or" the roll and extending outwardly from opposite endsof shell, bearing means receiving opposite ends of said beam member,means between said *beam and said shell for transmitting forces from thebeam to the shell, first conduit means connected to a source of hotfluid for applying heat to an axially extending portion of said beam,and second conduit means connected to a source of cooling fluid forwithdrawing heat from an axially extending portion of the beam that isradially spaced from the axially extending portion of the beam that isheated, thereby to distort the beam and deflect the shell in oppositionto such deflection.

References Cited in the file of this patent UNITED STATES PATENTS1,996,500 Adams Apr. 2, 1935 2,547,975 Robertson Apr. 10, 1951 2,970,339Hausman Feb. 7, 1961

2. APPARATUS FOR CONTROLLING DEFLECTION IN A ROLL MEMBER, COMPRISING ATHERMALLY EXPANSIBLE SUPPORT MEMBER COEXTENSIVE WITH AND MOUNTING SAIDROLL MEMBER, AND FIRST CONDUIT MEANS FOR APPLYING HEAT TO AN AXIALLYEXTENDING PORTION OF SAID SUPPORT MEMBER AND SECOND CONDUIT MEANS FORWITHDRAWING HEAT FROM ANOTHER RADIALLY SPACED AXIALLY EXTENDING PORTIONOF SAID SUPPORT MEMBER, THEREBY TO DEFLECT THE SUPPORT MEMBER AND IMPARTA DEFLECTING FORCE TO SAID ROLL MEMBER.